Multi-speed transmission

ABSTRACT

A transmission of the present invention has an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices may include clutches and brakes. The torque transmitting devices are each selectively engageable in combinations of at least three to establish a plurality forward speed ratios and at least one reverse speed ratio.

FIELD

The invention relates generally to a multiple speed transmission havinga plurality of planetary gear sets and a plurality of torquetransmitting devices, and more particularly to a transmission having aplurality speeds, four planetary gear sets and a plurality of torquetransmitting devices.

BACKGROUND

The statements in this section merely provide background informationrelated to the present disclosure and may or may not constitute priorart.

A typical multiple speed transmission uses a combination of frictionclutches or brakes, planetary gear arrangements and fixedinterconnections to achieve a plurality of gear ratios. The number andphysical arrangement of the planetary gear sets, generally, are dictatedby packaging, cost and desired speed ratios.

While current transmissions achieve their intended purpose, the need fornew and improved transmission configurations which exhibit improvedperformance, especially from the standpoints of efficiency,responsiveness and smoothness and improved packaging, primarily reducedsize and weight, is essentially constant. Accordingly, there is a needfor an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member,four planetary gear sets, a plurality of coupling members and aplurality of torque transmitting devices. Each of the planetary gearsets includes first, second and third members. The torque transmittingdevices are for example clutches and brakes.

In an aspect of the present invention, an output member continuouslyinterconnected with the ring gear of the third planetary gear set andthe carrier member of the fourth planetary gear set.

In another aspect of the present invention, a transmission is providedhaving a first interconnecting member for continuously interconnectingthe carrier member of the first planetary gear set with the carriermember of the second planetary gear set.

In yet another aspect of the present invention, a transmission isprovided having a second interconnecting member for continuouslyinterconnecting the ring gear of the first planetary gear set with thering gear of the second planetary gear set, the sun gear of the fourthplanetary gear set and the sun gear of the third planetary gear set.

In yet another aspect of the present invention, a transmission isprovided having a third interconnecting member for continuouslyinterconnecting the ring gear of the third planetary gear set with thecarrier member of the fourth planetary gear set.

In yet another aspect of the present invention, a transmission isprovided having a first torque transmitting device for selectivelyengaging the carrier member of the second planetary gear set and thecarrier member of the first planetary gear set with the input member.

In yet another aspect of the present invention, a transmission isprovided having a second torque transmitting device for selectivelyengaging the sun gear of the first planetary gear set with the inputmember.

In yet another aspect of the present invention, a transmission isprovided having a third torque transmitting device for selectivelyengaging the carrier member of the third planetary gear set with theinput member.

In yet another aspect of the present invention, a transmission isprovided having a fourth torque transmitting device for selectivelyengaging the sun gear member of the second planetary gear set with astationary member.

In yet another aspect of the present invention, a transmission isprovided having a fifth torque transmitting device for selectivelyengaging the carrier member of the first planetary gear set with thestationary member.

In yet another aspect of the present invention, a transmission isprovided having a sixth torque transmitting device for selectivelyengaging the sun gear of the first planetary gear set with thestationary member.

In yet another aspect of the present invention, a transmission isprovided having a seventh torque transmitting device for selectivelyengaging the ring gear of the fourth planetary gear set with thestationary member.

In still another aspect of the present invention, the torquetransmitting devices are each selectively engageable in combinations ofat least three to establish a plurality forward speed ratios and atleast one reverse speed ratio between the input member and the outputmember.

In still another aspect of the present invention, the carrier member ofthe second planetary gear set rotatable supports a first and second setof planet pinions and the first set of planet pinions mesh with the sungear and the second set of planet pinions and the second set of planetpinions mesh with the ring gear and the first set of planet pinions.

Further features, aspects and advantages of the present invention willbecome apparent by reference to the following description and appendeddrawings wherein like reference numbers refer to the same component,element or feature.

DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of an eleven speedtransmission according to the present invention;

FIG. 2 is a diagrammatic view of an embodiment of an eleven speedtransmission according to the present invention;

FIG. 3 is a diagrammatic view of another embodiment of an eleven speedtransmission according to the present invention; and

FIG. 4 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the transmission illustrated inFIGS. 1, 2 and 3.

DETAILED DESCRIPTION

The following description is merely exemplary in nature and is notintended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that in the particular exampleprovided, the eleven speed automatic transmission of the presentinvention has an arrangement of permanent mechanical connections betweenthe elements of the four planetary gear sets. A second component orelement of a first planetary gear set is permanently coupled to a firstcomponent or element of a second planetary gear set. A third componentor element of the first planetary gear set is permanently coupled to asecond component or element of a second planetary gear set and to afirst component or element of a fourth planetary gear set and to a firstcomponent or element of a third planetary gear set. A second componentor element of a fourth planetary gear set is permanently coupled to athird component or element of a third planetary gear set and to theoutput member.

Referring now to FIG. 1, an embodiment of an eleven speed transmission10 is illustrated in a lever diagram format. A lever diagram is aschematic representation of the components of a mechanical device suchas an automatic transmission. Each individual lever represents aplanetary gear set wherein the three basic mechanical components of theplanetary gear set are each represented by a node. Therefore, a singlelever contains three nodes: one for the sun gear, one for the planetgear carrier and one for the ring gear. The relative length between thenodes of each lever can be used to represent the ring-to-sun ratio ofeach respective gear set. These lever ratios, in turn, are used to varythe gear ratios of the transmission in order to achieve appropriateratios and ratio progression. Mechanical couplings or interconnectionsbetween the nodes of the various planetary gear sets are illustrated bythin, horizontal lines and torque transmitting devices such as clutchesand brakes are presented as interleaved fingers. If the device is abrake, one set of the fingers is grounded. Further explanation of theformat, purpose and use of lever diagrams can be found in SAE Paper810102, “The Lever Analogy: A New Tool in Transmission Analysis” byBenford and Leising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, a firstplanetary gear set 14 having three nodes: a first node 14A, a secondnode 14B and a third node 14C, a second planetary gear set 16 havingthree nodes: a first node 16A, a second node 16B and a third node 16C, athird planetary gear set 18 having three nodes: a first node 18A, asecond node 18B and a third node 18C, a fourth planetary gear set 20having three nodes: a first node 20A, a second node 20B and a third node20C and an output shaft or member 22.

The second node 14B of the first planetary gear set 14 is coupled to afirst node 16A of the second planetary gear set 16. The second node 16Bof the second planetary gear set 16 is coupled to third node 14C of thefirst planetary gear set 14. The third node 14C of the first planetarygear set 14 is coupled to the first node 20A of the fourth planetarygear set 20. The first node 20A of the fourth planetary gear set 20 iscoupled to the first node 18A of the third planetary gear set 18. Thethird node 18C of the third planetary gear set 18 is coupled to thesecond node 20B of the fourth planetary gear set 20 and to the outputshaft or member 22.

A first clutch 26 selectively connects the first node 16A of the secondplanetary gear set 16 and the second node 14B of the first planetarygear set 14 with the input shaft or member 12. A second clutch 28selectively connects the first node 14A of the first planetary gear set14 with the input shaft or member 12. A third clutch 30 selectivelyconnects the second node 18B of the third planetary gear set 18 with theinput shaft or member 12. A first brake 32 selectively connects thethird node 16C of the second planetary gear set 16 with the stationaryelement or a transmission housing 50. A second brake 34 selectivelyconnects the second node 14B of the first planetary gear set 14 with thestationary element or a transmission housing 50. A third brake 36selectively connects the first node 14A of the first planetary gear set14 with the stationary element or a transmission housing 50. A fourthbrake 38 selectively connects the third node 20C of the fourth planetarygear set 20 with the stationary element or a transmission housing 50.

Referring now to FIG. 2, a stick diagram presents a schematic layout ofthe embodiment of the eleven speed transmission 10 according to thepresent invention. In FIG. 2, the numbering from the lever diagram ofFIG. 1 is carried over. The clutches, brakes, and couplings arecorrespondingly presented whereas the nodes of the planetary gear setsnow appear as components of planetary gear sets such as sun gears, ringgears, planet gears and planet gear carriers.

For example, the planetary gear set 14 includes a sun gear member 14A, aring gear member 14C and a planet gear carrier member 14B that rotatablysupports a set of planet gears 14D (only one of which is shown). The setof planet gears 14D are each configured to intermesh with both the sungear member 14A and a ring gear member 14C. The sun gear member 14A isconnected for common rotation with a first shaft or interconnectingmember 42. The ring gear member 14C is connected for common rotationwith a second shaft or interconnecting member 44 and with a third shaftor interconnecting member 46. The planet carrier member 14B is connectedfor common rotation with a fourth shaft or interconnecting member 48 andwith a fifth shaft or interconnecting member 52.

The planetary gear set 16 includes a sun gear member 16C, a ring gearmember 16B and a planet gear carrier member 16A that rotatably supportsa first set of planet gears 16D (only one of which is shown) and asecond set of planet gears 16E (only one of which is shown). The firstset of planet gears 16D are each configured to intermesh with both thesun gear member 16C and the second set of planet gears 16E. The secondset of planet gears 16E are each configured to intermesh with both thering gear member 16B and the first set of planet gears 16D. The sun gearmember 16C is connected for common rotation with a sixth shaft orinterconnecting member 54. The ring gear member 16B is connected forcommon rotation with the second shaft or interconnecting member 44. Theplanet carrier member 16A is connected for common rotation with thefourth shaft or interconnecting member 48 and a seventh shaft orinterconnecting member 56.

The planetary gear set 18 includes a sun gear member 18A, a ring gearmember 18C and a planet gear carrier member 18B that rotatably supportsa set of planet gears 18D (only one of which is shown). The set ofplanet gears 18D are each configured to intermesh with both the sun gearmember 18A and the ring gear member 18C. The sun gear member 18A isconnected for common rotation with an eighth shaft or interconnectingmember 58. The ring gear member 18C is connected for common rotationwith a ninth shaft or interconnecting member 60 and with the outputshaft or member 22. The planet carrier member 18B is connected forcommon rotation with a tenth shaft or interconnecting member 62.

The planetary gear set 20 includes a sun gear member 20A, a ring gearmember 20C and a planet gear carrier member 20B that rotatably supportsa set of planet gears 20D (only one of which is shown). The set ofplanet gears 20D are each configured to intermesh with both the sun gearmember 20A and the ring gear member 20C. The sun gear member 20A isconnected for common rotation with the third shaft or interconnectingmember 46 and with the eighth shaft or interconnecting member 58. Thering gear member 20C is connected for common rotation with an eleventhshaft or interconnecting member 64. The planet carrier member 20B isconnected for common rotation with the ninth shaft or interconnectingmember 60.

The input shaft or member 12 is continuously connected to an engine (notshown) or to a turbine of a torque converter (not shown). The outputshaft or member 22 is continuously connected with the final drive unitor transfer case (not shown).

The torque-transmitting mechanisms or the clutches 26, 28, 30 and thebrakes 32, 34, 36 and 38 allow for selective interconnection of theshafts or interconnecting members, members of the planetary gear setsand the housing. For example, the first clutch 26 is selectivelyengageable to connect the fifth shaft or interconnecting member 52 withthe input shaft or member 12. The second clutch 28 is selectivelyengageable to connect the first shaft or interconnecting member 42 withthe input shaft or member 12. The third clutch 30 is selectivelyengageable to connect the tenth shaft or interconnecting member 62 withthe input shaft or member 12. The first brake 32 is selectivelyengageable to connect the sixth shaft or interconnecting member 54 withthe stationary element or the transmission housing 50 in order toprevent the sixth shaft or interconnecting member 54 from rotatingrelative to the transmission housing 50. The second brake 34 isselectively engageable to connect the seventh shaft or interconnectingmember 56 with a stationary element or the transmission housing 50 inorder to prevent the seventh shaft or interconnecting member 56 fromrotating relative to the transmission housing 50. The third brake 36 isselectively engageable to connect the first shaft or interconnectingmember 42 with the stationary element or the transmission housing 50 inorder to prevent the first shaft or interconnecting member 42 fromrotating relative to the transmission housing 50. The fourth brake 38 isselectively engageable to connect the eleventh shaft or interconnectingmember 64 with the stationary element or the transmission housing 50 inorder to prevent the eleventh shaft or interconnecting member 64 fromrotating relative to the transmission housing 50.

With reference to FIG. 3, an alternate embodiment of an eleven speedtransmission 100 of the present invention is illustrated schematically.Transmission 100 has the same number of planetary gear sets, clutchesand brakes interconnecting members of the planetary gear sets asindicated by like reference numbers depicting like components. However,transmission 100 replaces the planetary gear set 16 which is a compoundplanetary gear set with a simple planetary gear set 160. As describedabove, planetary gear set 16 is referred to as a compound planetary gearset because planetary gear set 16 has a carrier member that supports twosets of planet or pinion gears 16D and 16E. In contrast, the simpleplanetary gear set 160 has a carrier member 160B that rotatable supportsonly one set of planet gears or pinion gears 160D. Further, simpleplanetary gear set 160 has a sun gear 160C and a ring gear 160A.Moreover, interconnecting member 56 has been eliminated andinterconnecting member 48 has been reconfigured as interconnectingmember 48′. More specifically, interconnecting member 48′ now connectsthe ring gear member 160A to carrier member 14B and to the second brake34. Second brake 34 couples interconnecting member 48′ to the ground ortransmission housing 50. Accordingly, the number of otherinterconnecting members of transmissions 10 and 100 remain the same,however, the length and configuration or shape of the interconnectingmembers are modified as shown in FIG. 3 to make the required connectionsbetween the members of the planetary gear sets and the clutches andbrakes.

Referring now to FIGS. 2, 3 and 4, the operation of the embodiment ofthe eleven speed transmissions 10 and 100 will be described. It will beappreciated that the transmissions 10 and 100 are capable oftransmitting torque from the input shaft or member 12 to the outputshaft or member 22 in a plurality forward speed or torque ratios (elevenfor example) and at least one reverse speed or torque ratio. Eachforward and reverse speed or torque ratio is attained by engagement ofone or more of the torque-transmitting mechanisms (i.e. first clutch 26,second clutch 28, third clutch 30, first brake 32, second brake 34,third brake 36 and fourth brake 38), as will be explained below. FIG. 4is a truth table presenting the various combinations oftorque-transmitting elements that are activated or engaged to achievethe various gear states. Actual numerical gear ratios of the variousgear states are also presented although it should be appreciated thatthese numerical values are exemplary only and that they may be adjustedover significant ranges to accommodate various applications andoperational criteria of the transmissions 10 and 100. An example of thegear ratios that may be obtained using the embodiments of the presentinvention are also shown in FIG. 4. Of course, other gear ratios areachievable depending on the gear diameter, gear teeth count and gearconfiguration selected.

With respect to transmission 10, a reverse gear is established byengaging or activating, the second clutch 28, the second brake 34 andfourth brake 38. The second clutch 28 connects the first shaft orinterconnecting member 42 with the input shaft or member 12. The secondbrake 34 connects the seventh shaft or interconnecting member 56 with astationary element or the transmission housing 50 in order to preventthe seventh shaft or interconnecting member 56 from rotating relative tothe transmission housing 50. The fourth brake 38 connects the eleventhshaft or interconnecting member 64 with the stationary element or thetransmission housing 50 in order to prevent the eleventh shaft orinterconnecting member 64 from rotating relative to the transmissionhousing 50. Likewise, the eleven forward ratios are achieved throughdifferent combinations of clutch and brake engagement, as shown in FIG.4.

With respect to transmission 100, a reverse gear is established byengaging or activating, the first clutch 26, the second brake 34 andfourth brake 38. The first clutch 26 connects the fifth shaft orinterconnecting member 52 with the input shaft or member 12. The secondbrake 34 connects the fourth shaft or interconnecting member 48′ with astationary element or the transmission housing 50 in order to preventthe fourth shaft or interconnecting member 48′ from rotating relative tothe transmission housing 50. The fourth brake 38 connects the eleventhshaft or interconnecting member 64 with the stationary element or thetransmission housing 50 in order to prevent the eleventh shaft orinterconnecting member 64 from rotating relative to the transmissionhousing 50. Likewise, the eleven forward ratios are achieved throughdifferent combinations of clutch and brake engagement, as shown in FIG.4.

It will be appreciated that the foregoing explanation of operation andgear states of the eleven speed transmissions 10 and 100 assumes, firstof all, that all the clutches and brakes not specifically referenced ina given gear state are inactive or disengaged and, second of all, thatduring gear shifts, i.e., changes of gear state, between at leastadjacent gear states, a clutch or brake engaged or activated in bothgear states will remain engaged or activated.

The description of the invention is merely exemplary in nature andvariations that do not depart from the spirit of the invention areintended to be within the scope of the invention. Such variations arenot to be regarded as a departure from the spirit and scope of theinvention.

What is claimed is:
 1. A transmission comprising: an input member; anoutput member; first, second, third and fourth planetary gear sets eachhaving first, second and third members; a first interconnecting membercontinuously interconnecting the second member of the first planetarygear set with the first member of the second planetary gear set; asecond interconnecting member continuously interconnecting the thirdmember of the first planetary gear set with the second member of thesecond planetary gear set, the first member of the fourth planetary gearset and the first member of the third planetary gear set; a thirdinterconnecting member continuously interconnecting the third member ofthe third planetary gear set with the second member of the fourthplanetary gear set; and seven torque transmitting devices eachselectively engageable to interconnect at least one of the first,second, and third members with at least one other of the first members,second members, third members and a stationary member, and wherein thetorque transmitting devices are selectively engageable in combinationsof at least three to establish a plurality forward speed ratios and atleast one reverse speed ratio between the input member and the outputmember.
 2. The transmission of claim 1 wherein a first of the seventorque transmitting devices is selectively engageable to interconnectthe first member of the second planetary gear set and the second memberof the first planetary gear set with the input member.
 3. Thetransmission of claim 2 wherein a second of the seven torquetransmitting devices is selectively engageable to interconnect the firstmember of the first planetary gear set with the input member.
 4. Thetransmission of claim 3 wherein a third of the seven torque transmittingdevices is selectively engageable to interconnect the second member ofthe third planetary gear set with the input member.
 5. The transmissionof claim 4 wherein a fourth of the seven torque transmitting devices isselectively engageable to interconnect the third member of the secondplanetary gear set with the stationary member.
 6. The transmission ofclaim 5 wherein a fifth of the seven torque transmitting devices isselectively engageable to interconnect the second member of the firstplanetary gear set with the stationary member.
 7. The transmission ofclaim 6 wherein a sixth of the seven torque transmitting devices isselectively engageable to interconnect the first member of the firstplanetary gear set with the stationary member.
 8. The transmission ofclaim 7 wherein a seventh of the seven torque transmitting devices isselectively engageable to interconnect the third member of the fourthplanetary gear set with the stationary member.
 9. The transmission ofclaim 1 wherein the first and fourth planetary gear sets are disposedbetween the second and third planetary gear sets.
 10. The transmissionof claim 1 wherein the first planetary gear set is disposed adjacent thesecond planetary gear set and the third planetary gear set is disposedadjacent the fourth planetary gear set.
 11. The transmission of claim 1wherein the first member of the first planetary gear set, the thirdmember of the second planetary gear set, the first member of the thirdplanetary gear set and the first member of the fourth planetary gear setare sun gears, the second member of the first planetary gear set, thefirst member of the second planetary gear set, the second member of thethird planetary gear set and the second member of the fourth planetarygear set are carrier members wherein the carrier member of the secondplanetary gear set rotatable supports a first and second set of planetpinions and wherein the first set of planet pinions mesh with the sungear and the second set of planet pinions and the second set of planetpinions mesh with the ring gear and the first set of planet pinions andthe third member of the first planetary gear set, second member of thesecond planetary gear set, the third member of the third planetary gearset and the third member of the fourth planetary gear set are ringgears.
 12. The transmission of claim 1 wherein output member iscontinuously interconnected with the third member of the third planetarygear set and with the second member of the fourth planetary gear set.13. The transmission of claim 1 wherein four of the seven torquetransmitting devices are brakes and three of the seven torquetransmitting devices are clutches.
 14. The transmission of claim 1wherein the stationary member is a transmission housing.
 15. Atransmission comprising: an input member; an output member; first,second, third and fourth planetary gear sets each having first, secondand third members, output member is continuously interconnected thethird member of the third planetary gear set and with the second memberof the fourth planetary gear set; a first interconnecting membercontinuously interconnecting the second member of the first planetarygear set with the first member of the second planetary gear set; asecond interconnecting member continuously interconnecting the thirdmember of the first planetary gear set with the second member of thesecond planetary gear set, the first member of the fourth planetary gearset and the first member of the third planetary gear set; a thirdinterconnecting member continuously interconnecting the third member ofthe third planetary gear set with the second member of the fourthplanetary gear set; a first torque transmitting device selectivelyengageable to interconnect the first member of the second planetary gearset and the second member of the first planetary gear set with the inputmember; a second torque transmitting device selectively engageable tointerconnect the first member of the first planetary gear set with theinput member; a third torque transmitting device selectively engageableto interconnect the second member of the third planetary gear set withthe input member; a fourth torque transmitting device selectivelyengageable to interconnect the third member of the second planetary gearset with a stationary member; a fifth torque transmitting deviceselectively engageable to interconnect the second member of the firstplanetary gear set with the stationary member; a sixth torquetransmitting device selectively engageable to interconnect the firstmember of the first planetary gear set with the stationary member; and aseventh torque transmitting device selectively engageable tointerconnect the third member of the fourth planetary gear set with thestationary member, and wherein the torque transmitting devices are eachselectively engageable in combinations of at least three to establish aplurality forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.
 16. The transmission ofclaim 15 wherein the first member of the first planetary gear set, thethird member of the second planetary gear set, the first member of thethird planetary gear set and the first member of the fourth planetarygear set are sun gears, the second member of the first planetary gearset, the first member of the second planetary gear set, the secondmember of the third planetary gear set and the second member of thefourth planetary gear set are carrier members wherein the carrier memberof the second planetary gear set rotatable supports a first and secondset of planet pinions and wherein the first set of planet pinions meshwith the sun gear and the second set of planet pinions and the secondset of planet pinions mesh with the ring gear and the first set ofplanet pinions and the third member of the first planetary gear set,second member of the second planetary gear set, the third member of thethird planetary gear set and the third member of the fourth planetarygear set are ring gears.
 17. The transmission of claim 15 wherein thefirst member of the first planetary gear set, the third member of thesecond planetary gear set, the first member of the third planetary gearset and the first member of the fourth planetary gear set are sun gears,the second member of the first planetary gear set, the second member ofthe second planetary gear set, the second member of the third planetarygear set and the second member of the fourth planetary gear set arecarrier members and the third member of the first planetary gear set,first member of the second planetary gear set, the third member of thethird planetary gear set and the third member of the fourth planetarygear set are ring gears.
 18. The transmission of claim 15 wherein thestationary member is a transmission housing.
 19. The transmission ofclaim 15 wherein the first and fourth planetary gear sets are disposedbetween the second and third planetary gear sets.
 20. The transmissionof claim 15 wherein the first planetary gear set is disposed adjacentthe second planetary gear set and the third planetary gear set isdisposed adjacent the fourth planetary gear set.
 21. A transmissioncomprising: an input member; an output member; first, second, third andfourth planetary gear sets each having a sun gear, a carrier member anda ring gear, output member is continuously interconnected the ring gearof the third planetary gear set and with the carrier member of thefourth planetary gear set; a first interconnecting member continuouslyinterconnecting the carrier member of the first planetary gear set withthe carrier member of the second planetary gear set; a secondinterconnecting member continuously interconnecting the ring gear of thefirst planetary gear set with the ring gear of the second planetary gearset, the sun gear of the fourth planetary gear set and the sun gear ofthe third planetary gear set; a third interconnecting membercontinuously interconnecting the ring gear of the third planetary gearset with the carrier member of the fourth planetary gear set; a firsttorque transmitting device selectively engageable to interconnect thecarrier member of the second planetary gear set and the carrier memberof the first planetary gear set with the input member; a second torquetransmitting device selectively engageable to interconnect the sun gearof the first planetary gear set with the input member; a third torquetransmitting device selectively engageable to interconnect the carriermember of the third planetary gear set with the input member; a fourthtorque transmitting device selectively engageable to interconnect thesun gear member of the second planetary gear set with a stationarymember; a fifth torque transmitting device selectively engageable tointerconnect the carrier member of the first planetary gear set with thestationary member; a sixth torque transmitting device selectivelyengageable to interconnect the sun gear of the first planetary gear setwith the stationary member; and a seventh torque transmitting deviceselectively engageable to interconnect the ring gear of the fourthplanetary gear set with the stationary member, and wherein the torquetransmitting devices are each selectively engageable in combinations ofat least three to establish at least eleven forward speed ratios and atleast one reverse speed ratio between the input member and the outputmember.
 22. A transmission comprising: an input member; an outputmember; first, second, third and fourth planetary gear sets each havinga sun gear, a carrier member and a ring gear, output member iscontinuously interconnected the ring gear of the third planetary gearset and with the carrier member of the fourth planetary gear set; afirst interconnecting member continuously interconnecting the carriermember of the first planetary gear set with the ring gear of the secondplanetary gear set; a second interconnecting member continuouslyinterconnecting the ring gear of the first planetary gear set with thecarrier member of the second planetary gear set, the sun gear of thefourth planetary gear set and the sun gear of the third planetary gearset; a third interconnecting member continuously interconnecting thering gear of the third planetary gear set with the carrier member of thefourth planetary gear set; a first torque transmitting deviceselectively engageable to interconnect the carrier member of the firstplanetary gear set and the ring gear of the second planetary gear setwith the input member; a second torque transmitting device selectivelyengageable to interconnect the sun gear of the first planetary gear setwith the input member; a third torque transmitting device selectivelyengageable to interconnect the carrier member of the third planetarygear set with the input member; a fourth torque transmitting deviceselectively engageable to interconnect the sun gear member of the secondplanetary gear set with a stationary member; a fifth torque transmittingdevice selectively engageable to interconnect the carrier member of thefirst planetary gear set and the ring gear of the second planetary gearset with the stationary member; a sixth torque transmitting deviceselectively engageable to interconnect the sun gear of the firstplanetary gear set with the stationary member; and a seventh torquetransmitting device selectively engageable to interconnect the ring gearof the fourth planetary gear set with the stationary member, and whereinthe torque transmitting devices are each selectively engageable incombinations of at least three to establish at least eleven forwardspeed ratios and at least one reverse speed ratio between the inputmember and the output member.